Multi-speed transmission

ABSTRACT

A transmission is provided having an input member, an output member, four planetary gear sets, a plurality of coupling members and a plurality of torque transmitting devices. Each of the planetary gear sets includes first, second and third members. The torque transmitting devices include clutches and brakes.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application claims the benefit of U.S. Provisional Application No. 61/023,675, filed on Jan. 25, 2008. The disclosure of the above application is incorporated herein by reference.

FIELD

The invention relates generally to a multiple speed transmission having a plurality of planetary gear sets and a plurality of torque transmitting devices and more particularly to a transmission having nine or more speeds, four planetary gear sets and a plurality of torque transmitting devices.

BACKGROUND

The statements in this section merely provide background information related to the present disclosure and may or may not constitute prior art.

A typical multiple speed transmission uses a combination of friction clutches, planetary gear arrangements and fixed interconnections to achieve a plurality of gear ratios. The number and physical arrangement of the planetary gear sets, generally, are dictated by packaging, cost and desired speed ratios.

While current transmissions achieve their intended purpose, the need for new and improved transmission configurations which exhibit improved performance, especially from the standpoints of efficiency, responsiveness and smoothness and improved packaging, primarily reduced size and weight, is essentially constant. Accordingly, there is a need for an improved, cost-effective, compact multiple speed transmission.

SUMMARY

A transmission is provided having an input member, an output member, four planetary gear sets, a plurality of coupling members and a plurality of torque transmitting devices. Each of the planetary gear sets includes first, second and third members. The torque transmitting devices are for example clutches and brakes.

Moreover, a first interconnecting member continuously interconnects the sun gear of the first planetary gear set with the sun gear of the second planetary gear set. A second interconnecting member continuously interconnects the ring gear of the first planetary gear set with a stationary member. A third interconnecting member continuously interconnects the carrier member of the first planetary gear set with the ring gear of the third planetary gear set. A fourth interconnecting member continuously interconnects the carrier member of the second planetary gear set with the sun gear of the third planetary gear set. A fifth interconnecting member continuously interconnects the carrier member of the third planetary gear set with the ring gear of the fourth planetary gear set.

Further, a first torque transmitting mechanism is selectively engageable to interconnect the input member with the sun gear of the fourth planetary gear set. A second torque transmitting mechanism is selectively engageable to interconnect the input member with the carrier member of the second planetary gear set. A third torque transmitting mechanism is selectively engageable to interconnect the input member with the ring gear of the second planetary gear set. A fourth torque transmitting mechanism is selectively engageable to interconnect the ring gear of the second planetary gear set with the carrier member of the fourth planetary gear set. A fifth torque transmitting mechanism selectively is engageable to interconnect the carrier member of the second planetary gear set with the stationary element. A sixth torque transmitting mechanism is selectively engageable to interconnect the sun gear of the first planetary gear set with the stationary element. The torque transmitting mechanisms are selectively engageable in combinations of at least three to establish at least nine forward speed ratios and at least one reverse speed ratio between the input member and the output member.

Additionally, an imaginary plane is disposed perpendicular to an input member axis and between an end of the input member and the planetary gear sets, and the fourth planetary gear set is adjacent the imaginary plane and the first planetary gear set is remote from the imaginary plane, the second planetary gear set is adjacent the fourth planetary gear set and the third planetary gear set is disposed between the second planetary gear set and first planetary gear set. The input member and output member are disposed parallel to each other and both intersect the imaginary plane.

In another aspect of the present invention, a transmission is provided having an input member, an output member, four planetary gear sets, a plurality of coupling members and a plurality of torque transmitting devices. Each of the planetary gear sets includes first, second and third members. The torque transmitting devices are for example clutches and brakes.

Moreover, an imaginary plane is disposed perpendicular to an input member axis and between an end of the input member and the planetary gear sets, and the second planetary gear set is adjacent to the imaginary plane and the fourth planetary gear set is remote from the imaginary plane, the third planetary gear set is adjacent the fourth planetary gear set and the first planetary gear set is disposed between the second planetary gear set and first planetary gear set. The input member and output member are axially aligned and only the input member intersects the imaginary plane.

Further objects, aspects and advantages of the present invention will become apparent by reference to the following description and appended drawings wherein like reference numbers refer to the same component, element or feature.

DRAWINGS

The drawings described herein are for illustration purposes only and are not intended to limit the scope of the present disclosure in any way.

FIG. 1 is a lever diagram of an embodiment of a nine speed transmission according to the present invention;

FIG. 2 is a diagrammatic illustration of an embodiment of a nine speed transmission according to the present invention;

FIG. 3 is a diagrammatic illustration of another embodiment of a nine speed transmission according to the present invention; and

FIG. 4 is a truth table presenting the state of engagement of the various torque transmitting elements in each of the available forward and reverse speeds or gear ratios of the transmissions illustrated in FIGS. 2 and 3.

DETAILED DESCRIPTION

The following description is merely exemplary in nature and is not intended to limit the present disclosure, application, or uses.

At the outset, it should be appreciated that the embodiments of the nine speed automatic transmission of the present invention have an arrangement of permanent mechanical connections between the elements of the four planetary gear sets. A first component or element of a first planetary gear set is permanently coupled to a ground or stationary structural member of the transmission. A second component or element of the first planetary gear set is permanently coupled to a third component or element of the third planetary gear set. A third component or element of the first planetary gear set is permanently coupled to a third component or element of the second planetary gear set. A second component or element of the second planetary gear set is permanently coupled to a first component or element of the third planetary gear set. A second component or element of the third planetary gear set is permanently coupled to a first component or element of the fourth planetary gear set.

Referring now to FIG. 1, an embodiment of a nine speed transmission 10 is illustrated in a lever diagram format. A lever diagram is a schematic representation of the components of a mechanical device such as an automatic transmission. Each individual lever represents a planetary gear set wherein the three basic mechanical components of the planetary gear are each represented by a node. Therefore, a single lever contains three nodes: one for the sun gear, one for the planet gear carrier, and one for the ring gear. The relative length between the nodes of each lever can be used to represent the ring-to-sun ratio of each respective gear set. These lever ratios, in turn, are used to vary the gear ratios of the transmission in order to achieve an appropriate ratios and ratio progression. Mechanical couplings or interconnections between the nodes of the various planetary gear sets are illustrated by thin, horizontal lines and torque transmitting devices such as clutches and brakes are presented as interleaved fingers. Further explanation of the format, purpose and use of lever diagrams can be found in SAE Paper 810102, “The Lever Analogy: A New Tool in Transmission Analysis” by Benford and Leising which is hereby fully incorporated by reference.

The transmission 10 includes an input shaft or member 12, a first planetary gear set 14 having three nodes: a first node 14A, a second node 14B and a third node 14C, a second planetary gear set 16 having three nodes: a first node 16A, a second node 16B and a third node 16C, a third planetary gear set 18 having three nodes: a first node 18A, a second node 18B and a third node 18C, a fourth planetary gear set 20 having three nodes: a first node 20A, a second node 20B and a third node 20C and an output shaft or member 22.

The input member 12 is selectively coupled to one of the first node 16A of the second planetary gear set 16, the second node 16B of the second planetary gear set 16 and to third node 20C of the fourth planetary gear set 20. The output member 22 is coupled to the second node 20B of the fourth planetary gear set 20. The first node 14A of the first planetary gear set 14 is coupled to ground or a transmission housing 50. The second node 14B of the first planetary gear set 14 is coupled to the third node 18C of the third planetary gear set 18. The third node 14C of the first planetary gear set 14 is coupled to the third node 16C of the second planetary gear set 16. The second node 16B of the second planetary gear set 16 is coupled to the first node 18A of the third planetary gear set 18. The second node 18B of the third planetary gear set 18 is coupled to the first node 20A of the fourth planetary gear set 20.

A first clutch 26 selectively connects the input shaft or member 12 with the third node 20C of the fourth planetary gear set 20. A second clutch 28 selectively connects the input shaft or member 12 with the second node 16B of the second planetary gear set 16. A third clutch 30 selectively connects the input shaft or member 12 with the first node 16A of the second planetary gear set 16. A fourth clutch 32 selectively connects the first node 16A of the second planetary gear set 16 with the second node 20B of the fourth planetary gear set 20 and with the output shaft or member 22. A first brake 34 selectively connects the first node 18A of the third planetary gear set 18 to a stationary member or transmission housing 50. A second brake 36 selectively connects the third node 14C of the first planetary gear set 14 to a stationary member or transmission housing 50.

Referring now to FIG. 2, a stick diagram presents a schematic layout of the embodiment of the nine speed transmission 10 according to the present invention. In FIG. 2, the numbering from the lever diagram of FIG. 1 is carried over. The clutches and couplings are correspondingly presented whereas the nodes of the planetary gear sets now appear as components of planetary gear sets such as sun gears, ring gears, planet gears and planet gear carriers.

For example, the planetary gear set 14 includes a sun gear member 14C, a ring gear member 14A and a planet gear carrier member 14B that rotatably supports a set of planet gears 14D (only one of which is shown). The sun gear member 14C is connected for common rotation with a first shaft or intermediate member 42 and a second shaft or intermediate member 44. The ring gear member 14A is connected to ground or transmission housing 50 through a third shaft or intermediate member 46. The planet carrier member 14B is connected for common rotation with a fourth shaft or intermediate member 48. The set of planet gears 14D are configured to intermesh with both the sun gear member 14C and ring gear member 14A.

The planetary gear set 16 includes a sun gear member 16C, a ring gear member 16A and a planet gear carrier member 16B that rotatably supports a set of planet gears 16D (only one of which is shown). The sun gear member 16C is connected for common rotation with the second shaft or intermediate member 44. The ring gear member 16A is connected for common rotation with a fifth shaft or intermediate member 52. The planet carrier member 16B is connected for common rotation with a sixth shaft or intermediate member 54 and a seventh shaft or intermediate member 56. The planet gears 16D are configured to intermesh with both the sun gear member 16C and the ring gear member 16A.

The planetary gear set 18 includes a sun gear member 18A, a ring gear member 18C and a planet gear carrier member 18B that rotatably supports a set of planet gears 18D (only one of which is shown). The sun gear member 18A is connected for common rotation with seventh shaft or intermediate member 56. The ring gear member 18C is connected for common rotation with fourth shaft or intermediate member 48. The planet carrier member 18B is connected for common rotation with an eighth shaft or intermediate 58. The planet gears 18D are configured to intermesh with both the sun gear member 18A and the ring gear member 18C.

The planetary gear set 20 includes a sun gear member 20C, a ring gear member 20A and a planet gear carrier member 20B that rotatably supports a set of planet gears 20D (only one of which is shown). The sun gear member 20C is connected for common rotation with a ninth shaft or intermediate member 60. The ring gear member 20A is connected for common rotation with eighth shaft or intermediate member 58. The planet carrier member 20B is connected for common rotation with a tenth shaft or intermediate member 62 and output shaft or member 22. The planet gears 20D are configured to intermesh with both the sun gear member 20C and the ring gear member 20A.

The input shaft or member 12 is continuously connected to an engine (not shown) or to a turbine of a torque converter (not shown). The output shaft or member 22 is continuously connected with the final drive unit or transfer case (not shown).

The torque-transmitting mechanisms or clutches 26, 28, 30, 32 and brakes 34 and 36 allow for selective interconnection of the shafts or interconnecting members, members of the planetary gear sets and the housing. For example, the first clutch 26 is selectively engageable to connect the input shaft or member 12 with the ninth shaft or intermediate member 60. The second clutch 28 is selectively engageable to connect the input shaft or member 12 with the sixth shaft or intermediate member 54. The third clutch 30 is selectively engageable to connect the input shaft or member 12 with the fifth shaft or intermediate member 52. The fourth clutch 32 is selectively engageable to connect the fifth shaft or intermediate member 52 with the tenth shaft or intermediate member 62. The first brake 34 is selectively engageable to connect the sixth shaft or intermediate member 54 with the stationary element or the transmission housing 50 in order to restrict the member 54 from rotating relative to the transmission housing 50. The second brake 36 is selectively engageable to connect the first shaft or intermediate member 42 with the stationary element or the transmission housing 50 in order to restrict the member 42 from rotating relative to the transmission housing 50.

Referring now to FIG. 3, a stick diagram presents a schematic layout of another embodiment of a nine speed transmission 10′ according to the present invention. In FIG. 3, the numbering from the lever diagram of FIG. 1 is carried over. Transmission 10′ has the same number of clutches and brakes and the same mechanical connections between the components of the planetary gear sets 14, 16, 18 and 20 as transmission 10. However, the ordering of the planetary gear sets and the configuration of the shafts or interconnecting members is different. For example in transmission 10′, if an imaginary reference plane P′ is drawn perpendicular to the input shaft 12′ and intersecting or crossing input shaft 12′, then the planetary gear set that is closest to plane P′ is the second planetary gear set 16′. Moving progressively farther from imaginary plane P′ are planetary gear sets 14′, 18′ and 20′. In contrast, transmission 10 has the fourth planetary gear set 20 closest to plane P and plane P intersects or crosses input shaft 12 and output shaft 22. Further, moving progressively farther from imaginary plane P in transmission 10 are positioned planetary gear sets 16, 18 and 14. Of course, the shafts or interconnecting members (42′, 44′, 46′, 48′, 52′, 54′, 56′, 58′, 60′ and 62′) of transmission 10′ will have a different configuration since the planetary gear sets are ordered differently. However, the shafts or interconnecting members (42′, 44′, 46′, 48′, 52′, 54′, 56′, 58′, 60′ and 62′) of transmission 10′ serve the same function as the corresponding interconnecting members (42, 44, 46, 48, 52, 54, 56, 58, 60 and 62) of transmission 10 and therefore have the same reference number with the addition of a prime symbol.

Referring now to FIG. 2, FIG. 3 and FIG. 4, the operation of the embodiments of the nine speed transmission 10 and 10′ will be described. It will be appreciated that transmission 10 and 10′ are capable of transmitting torque from the input shaft or member 12 and 12′ to the output shaft or member 22 and 22′ in at least nine forward speed or torque ratios and at least one reverse speed or torque ratio with a single overdrive. Each forward and reverse speed or torque ratio is attained by engagement of one or more of the torque-transmitting mechanisms (i.e. first clutch 26, second clutch 28, third clutch 30, fourth clutch 32, first brake 34 and second brake 36), as will be explained below. FIG. 4 is a truth table presenting the various combinations of torque-transmitting mechanisms that are activated or engaged to achieve the various gear states. An “X” in the box means that the particular clutch or brake is engaged to achieve the desired gear state. An “O” represents that the particular torque transmitting device (i.e. a brake or clutch) is on or active, but not carrying torque. Actual numerical gear ratios of the various gear states are also presented although it should be appreciated that these numerical values are exemplary only and that they may be adjusted over significant ranges to accommodate various applications and operational criteria of the transmission 10, 10′. An example of the gear ratios that may be obtained using the embodiments of the present invention are also shown in FIG. 4. Of course, other gear ratios are achievable depending on the gear diameter, gear teeth count and gear configuration selected.

To establish a reverse gear, the first clutch 26, third clutch 30 and first brake 34 are engaged or activated. The first clutch 26 connects the input shaft or member 12 with the ninth shaft or intermediate member 60. The third clutch 30 connects the input shaft or member 12 with the fifth shaft or intermediate member 52. The first brake 34 connects the sixth shaft or intermediate member 54 with the stationary element or the transmission housing 50 in order to restrict the member 54 from rotating relative to the transmission housing 50. Likewise, the nine forward ratios are achieved through different combinations of clutch and brake engagement, as shown in FIG. 4.

It will be appreciated that the foregoing explanation of operation and gear states of the nine speed transmission 10, 10′ assumes, first of all, that all the clutches not specifically referenced in a given gear state are inactive or disengaged and, second of all, that during gear shifts, i.e., changes of gear state, between at least adjacent gear states, a clutch engaged or activated in both gear states will remain engaged or activated.

The description of the invention is merely exemplary in nature and variations that do not depart from the gist of the invention are intended to be within the scope of the invention. Such variations are not to be regarded as a departure from the spirit and scope of the invention. 

1. A transmission comprising: an input member; an output member; first, second, third and fourth planetary gear sets each having first, second and third members, wherein the output member is continuously interconnected to the second member of the fourth planetary gear set; a first interconnecting member continuously interconnecting the third member of the first planetary gear set with the third member of the second planetary gear set; a second interconnecting member continuously interconnecting the first member of the first planetary gear set with a stationary member; a third interconnecting member continuously interconnecting the second member of the first planetary gear set with the third member of the third planetary gear set; a fourth interconnecting member continuously interconnecting the second member of the second planetary gear set with the first member of the third planetary gear set; a fifth interconnecting member continuously interconnecting the second member of the third planetary gear set with the first member of the fourth planetary gear set; and six torque transmitting mechanisms selectively engageable to interconnect one of the first, second, and third members with at least another of the first, second, third members and a stationary element, and wherein the torque transmitting mechanisms are selectively engageable in combinations of at least three to establish at least nine forward speed ratios and at least one reverse speed ratio between the input member and the output member, and wherein an imaginary plane is disposed perpendicular to an input member axis and between an end of the input member and the planetary gear sets, and the fourth planetary gear set is adjacent the imaginary plane and the first planetary gear set is remote from the imaginary plane, the second planetary gear set is adjacent the fourth planetary gear set and the third planetary gear set is disposed between the second planetary gear set and first planetary gear set.
 2. The transmission of claim 1 wherein the input member and output member are disposed parallel to each other and both intersect the imaginary plane.
 3. The transmission of claim 1 wherein a first of the six torque transmitting mechanisms is selectively engageable to interconnect the input member with the third member of the fourth planetary gear set.
 4. The transmission of claim 3 wherein a second of the six torque transmitting mechanisms is selectively engageable to interconnect the input member with the second member of the second planetary gear set.
 5. The transmission of claim 4 wherein a third of the six torque transmitting mechanisms is selectively engageable to interconnect the input member with the first member of the second planetary gear set.
 6. The transmission of claim 5 wherein a fourth of the six torque transmitting mechanisms is selectively engageable to interconnect the first member of the second planetary gear set with the second member of the fourth planetary gear set.
 7. The transmission of claim 6 wherein a fifth of the six torque transmitting mechanisms is selectively engageable to interconnect the second member of the second planetary gear set with the stationary element.
 8. The transmission of claim 7 wherein a sixth of the six torque transmitting mechanisms is selectively engageable to interconnect the third member of the first planetary gear set with the stationary element.
 9. The transmission of claim 1 wherein the third member of the first, second and fourth planetary gear sets and the first member of the third planetary gear set are sun gears, the second members of the first, second third and fourth planetary gear sets are carrier members, and the first members of the first, second and fourth planetary gear sets and the third member of the third planetary gear set are ring gears.
 10. The transmission of claim 1 wherein two of the torque transmitting mechanisms are brakes for connecting a plurality of the first, second, and third members to the stationary element and four of the torque transmitting mechanisms are clutches for connecting a set of the first, second, and third members to another set of the first, second, and third members.
 11. A transmission comprising: an input member; an output member; first, second, third and fourth planetary gear sets each having first, second and third members, wherein the output member is continuously interconnected to the second member of the fourth planetary gear set; a first interconnecting member continuously interconnecting the third member of the first planetary gear set with the third member of the second planetary gear set; a second interconnecting member continuously interconnecting the first member of the first planetary gear set with a stationary member; a third interconnecting member continuously interconnecting the second member of the first planetary gear set with the third member of the third planetary gear set; a fourth interconnecting member continuously interconnecting the second member of the second planetary gear set with the first member of the third planetary gear set; a fifth interconnecting member continuously interconnecting the second member of the third planetary gear set with the first member of the fourth planetary gear set; and six torque transmitting mechanisms selectively engageable to interconnect one of the first, second, and third members with at least another of the first, second, third members and a stationary element, and wherein the torque transmitting mechanisms are selectively engageable in combinations of at least three to establish at least nine forward speed ratios and at least one reverse speed ratio between the input member and the output member, and wherein an imaginary plane is disposed perpendicular to an input member axis and between an end of the input member and the planetary gear sets, and the second planetary gear set is adjacent the imaginary plane and the fourth planetary gear set is remote from the imaginary plane, the third planetary gear set is adjacent the fourth planetary gear set and the first planetary gear set is disposed between the second planetary gear set and third planetary gear set.
 12. The transmission of claim 11 wherein the input member and output member are axially aligned and only the input member intersects the imaginary plane.
 13. The transmission of claim 11 wherein a first of the six torque transmitting mechanisms is selectively engageable to interconnect the input member with the third member of the fourth planetary gear set.
 14. The transmission of claim 13 wherein a second of the six torque transmitting mechanisms is selectively engageable to interconnect the input member with the second member of the second planetary gear set.
 15. The transmission of claim 14 wherein a third of the six torque transmitting mechanisms is selectively engageable to interconnect the input member with the first member of the second planetary gear set.
 16. The transmission of claim 15 wherein a fourth of the six torque transmitting mechanisms is selectively engageable to interconnect the first member of the second planetary gear set with the second member of the fourth planetary gear set.
 17. The transmission of claim 16 wherein a fifth of the six torque transmitting mechanisms is selectively engageable to interconnect the second member of the second planetary gear set with the stationary element.
 18. The transmission of claim 17 wherein a sixth of the six torque transmitting mechanisms is selectively engageable to interconnect the third member of the first planetary gear set with the stationary element.
 19. The transmission of claim 11 wherein the third member of the first, second and fourth planetary gear sets and the first member of the third planetary gear set are sun gears, the second members of the first, second third and fourth planetary gear sets are carrier members, and the first members of the first, second and fourth planetary gear sets and the third member of the third planetary gear set are ring gears.
 20. The transmission of claim 11 wherein two of the torque transmitting mechanisms are brakes for connecting a plurality of the first, second, and third members to the stationary element and four of the torque transmitting mechanisms are clutches for connecting a set of the first, second, and third members to another set of the first, second, and third members.
 21. A transmission comprising: an input member; an output member; first, second, and third planetary gear sets each having sun gears, carrier members and ring gears, wherein the output member is continuously interconnected to the carrier member of the fourth planetary gear set; a first interconnecting member continuously interconnecting the sun gear of the first planetary gear set with the sun gear of the second planetary gear set; a second interconnecting member continuously interconnecting the ring gear of the first planetary gear set with a stationary member; a third interconnecting member continuously interconnecting the carrier member of the first planetary gear set with the ring gear of the third planetary gear set; a fourth interconnecting member continuously interconnecting the carrier member of the second planetary gear set with the sun gear of the third planetary gear set; a fifth interconnecting member continuously interconnecting the carrier member of the third planetary gear set with the ring gear of the fourth planetary gear set; a first torque transmitting mechanism selectively engageable to interconnect the input member with the sun gear of the fourth planetary gear set; a second torque transmitting mechanism selectively engageable to interconnect the input member with the carrier member of the second planetary gear set; a third torque transmitting mechanism selectively engageable to interconnect the input member with the ring gear of the second planetary gear set; a fourth torque transmitting mechanism selectively engageable to interconnect the ring gear of the second planetary gear set with the carrier member of the fourth planetary gear set; a fifth torque transmitting mechanism selectively engageable to interconnect the carrier member of the second planetary gear set with the stationary element; and a sixth torque transmitting mechanism selectively engageable to interconnect the sun gear of the first planetary gear set with the stationary element, wherein the torque transmitting mechanisms are selectively engageable in combinations of at least three to establish at least nine forward speed ratios and at least one reverse speed ratio between the input member and the output member, and wherein an imaginary plane is disposed perpendicular to an input member axis and between an end of the input member and the planetary gear sets, and the fourth planetary gear set is adjacent the imaginary plane and the first planetary gear set is remote from the imaginary plane, the second planetary gear set is adjacent the fourth planetary gear set and the third planetary gear set is disposed between the second planetary gear set and first planetary gear set, and wherein the input member and output member are disposed parallel to each other and both intersect the imaginary plane.
 22. A transmission comprising: an input member; an output member; first, second, and third planetary gear sets each having sun gears, carrier members and ring gears, wherein the output member is continuously interconnected to the carrier member of the fourth planetary gear set; a first interconnecting member continuously interconnecting the sun grear of the first planetary gear set with the sun gear of the second planetary gear set; a second interconnecting member continuously interconnecting the ring gear of the first planetary gear set with a stationary member; a third interconnecting member continuously interconnecting the carrier member of the first planetary gear set with the ring gear of the third planetary gear set; a fourth interconnecting member continuously interconnecting the carrier member of the second planetary gear set with the sun gear of the third planetary gear set; a fifth interconnecting member continuously interconnecting the carrier member of the third planetary gear set with the ring gear of the fourth planetary gear set; a first torque transmitting mechanism selectively engageable to interconnect the input member with the sun gear of the fourth planetary gear set; a second torque transmitting mechanism selectively engageable to interconnect the input member with the carrier member of the second planetary gear set; a third torque transmitting mechanism selectively engageable to interconnect the input member with the ring gear of the second planetary gear set; a fourth torque transmitting mechanism selectively engageable to interconnect the ring gear of the second planetary gear set with the carrier member of the fourth planetary gear set; a fifth torque transmitting mechanism selectively engageable to interconnect the carrier member of the second planetary gear set with the stationary element; and a sixth torque transmitting mechanism selectively engageable to interconnect the sun gear of the first planetary gear set with the stationary element, wherein the torque transmitting mechanisms are selectively engageable in combinations of at least three to establish at least nine forward speed ratios and at least one reverse speed ratio between the input member and the output member, and wherein an imaginary plane is disposed perpendicular to an input member axis and between an end of the input member and the planetary gear sets, and the second planetary gear set is adjacent to the imaginary plane and the fourth planetary gear set is remote from the imaginary plane, the third planetary gear set is adjacent the fourth planetary gear set and the first planetary gear set is disposed between the second planetary gear set and third planetary gear set, and wherein the input member and output member are axially aligned and only the input member intersects the imaginary plane. 